JP2010532850A - solenoid valve - Google Patents

Abstract

The present invention relates to a magnet structure group (13), a valve cartridge (22, 42) having magnetic poles (23, 43), and a valve insert (25, 45) connected to the magnetic poles (23, 43). ) And a movable element (24, 44) guided in a movable manner in the axial direction between the closed position and the open position in the valve insert (25, 45) and connected to the closing member (28, 48). And a main valve seat connected to the valve insert (25, 45) and disposed between at least one first through-opening (31, 51) and a second through-opening (32, 52) The movable element (24, 44) having a valve body (29, 49) provided with (30, 50) and movable in the axial direction is supplied with power to the magnet structure group (13). the valve insert (25, 45) force which is caused in the (F _Magnet) by a return spring (26, 46 Against the spring force of (F _Feder), and against the fluid force (F _Hydraulik), is moved in a direction toward the pole center (23, 43), whereby the closure member (28 and 48 ) Is lifted from the main valve seat (30, 50) to allow fluid flow between the at least one first flow-through opening (31, 51) and the second flow-through opening (32, 52). Further, the movable element (24, 44) movable in the axial direction is moved by the spring force (F _Feder ) of the return spring (26, 46) within the valve insert (25, 45). 43) is moved away from the closing member (28, 48) in an airtight manner into the main valve seat (30, 50), and the at least one first flow-through opening (31, 51). And the second through-flow opening (32, 52) Fluid flow is about of the type adapted to be suspended between. According to the present invention, the characteristic curve of the magnetic force (F _Magnet ), the characteristic curve of the spring force (F _Feder ) and the characteristic curve of the fluid force (F _Hydraulik ) over the stroke of the mover (24, ₄₄ ). At least one broadly representing a force balance point between the negative full power characteristic curve slope between the closed position and the open position of the mover (24, 44) and the closing member (28, 48). Combined so that a stable working point can be adjusted.

Description

  The invention relates to a solenoid valve of the type described in the superordinate conceptual part of claim 1.

For example, a conventional solenoid valve for a hydraulic device used in an anti-lock braking system (ABS) or a traction slip control system (ASR-System) or an electronic stability program system (ESP-System) is shown in FIG. Is shown in As shown in FIG. 1, a conventional electromagnetic valve 1 configured as a switching control valve and closed in a non-excited state includes a valve cartridge 2 and a magnet structure group 13. The valve cartridge 2 includes a magnetic pole core 3, a valve insert 5 connected to the magnetic pole core 3 and configured as a sleeve, and an axial direction between a closed position and an open position within the valve insert 5. The movable member 4 is movably guided and connected to the closing member 8, and has a valve body 9 connected to the valve insert and having a main valve seat 10. At least one first through-opening 11 and a second through-opening 12 are arranged. The magnet structure group 13 includes a winding support 13.1, a casing peripheral wall 13.2, a winding 13.3 having an electrical connection 13.5, and a cover disk 13.4. . The axially movable mover 4 is generated in the valve insert 5 when power is supplied to the magnet structure group 13, that is, when a current is applied to the winding via the electrical connection 13.5. The closing member 8 is lifted from the main valve seat 10 by moving it toward the magnetic core 3 against the spring force F _Feder of the return spring 6 and against the fluid force F _Hydraulik by the magnetic force F _Magnet . Allow fluid flow between two first through-openings 11 and second through-openings 12. The maximum possible stroke of the mover 4 or the closing member 8 is given in advance by the air gap 7 between the magnetic core 3 and the mover 4. Movable movable in the axial direction to airtightly press the closing member 8 into the main valve seat 10 and block the flow of fluid between the at least one first through-opening 11 and the second through-opening 12. The child 4 is moved together with the closing member 8 by the spring force F _Feder of the return spring 6 and by the fluid force F _Hydraulik in the valve insert 5 toward the main valve seat 10 in a direction away from the magnetic pole core 3. The magnetic pole core 3 is connected to the valve insert 5 in a fluid-tight manner, for example, by a welding seam. In addition, the illustrated solenoid valve 1 is caulked and coupled to the fluid device block 15 via the caulking flange 16. The action directions of the spring force F _Feder , the fluid force F _Hydraulik and the magnetic force F _Magnet are indicated by arrows in FIG. 1.

  The outlet valve in the ABS / ESP system is conventionally configured as a pure switching control valve, which is simply fully opened or closed completely in a semi-steady state. The outlet valve is adapted to flow in the closing stroke direction in a typical manner as a discontinuous switching control valve. This is based on the background that high wheel pressure promotes valve sealing. As a result, a small spring preload is sufficient, and as a result, a full power level is reduced, and a quick valve response is possible.

  In contrast to the switching control valve, the steady state valve is adjusted in an arbitrarily adjustable intermediate position by adjusting part of the stroke between the fully closed position and the fully open position, and thus any It has the advantage that the through-flow cross-section is opened or any through-flow rate is adjusted through the valve. This means that for the valves of the ABS / ESP system, the wheel pressure increase and depressurization curve slopes can be variably adjusted, thereby improving the wheel pressure meterability and generating noise. This means that the pressure oscillations that occur are reduced. However, steady valves that flow through in the open direction require a high spring preload to seal the required wheel pressure, for example the wheel pressure at the lock pressure level. This leads to very high full power levels, excessive current strength when powering the magnet structure group, which is disadvantageous in terms of valve reaction time, flow regulation accuracy and thermal characteristics.

DISCLOSURE OF THE INVENTION On the other hand, the solenoid valve according to the present invention having the characteristics described in the characterizing portion of the independent claim 1 is characterized in that a magnetic force characteristic curve, a spring force characteristic curve, and a fluid force At least one wide and stable working point, wherein the characteristic curve represents a force balance point with a negative full power characteristic curve gradient between the closed and open positions of the mover and the closure member It is characterized by being combined so that can be adjusted. Adjusting the stable working point in a solenoid valve configured as a switching control valve that flows through in the closing direction by specially selecting the characteristic curves of spring force, magnetic force and fluid force in relation to the valve stroke As a result, this electromagnetic valve can be driven as a steady valve. Thereby, the solenoid valve according to the present invention has the advantages of a steady valve, but at the same time the quick response of the switching control valve that flows through in the closing direction, at a reduced overall force level and at a pressure of any height. It also has advantages such as sealing properties.

  Advantageous embodiments and improvements of the solenoid valve according to the independent claim 1 are possible by means and embodiments as defined in the dependent claims.

  Particularly advantageously, the characteristic curve of the magnetic force over the stroke of the mover and the closing member, which is generated by supplying power to the structure of the solenoid valve according to the invention, is given by the given geometry of the mover and the pole core. Is adjusted to be as flat as possible. In order to be able to adjust any depressurization characteristic curve slope by means of the solenoid valve according to the invention, the current for feeding the magnet structure is controlled by a valve current regulator in relation to the pressure sensor signal. Moreover, the strength of the current for supplying power to the magnet structure group can be adjusted without a pressure sensor. Therefore, the mover, together with the closing member, is moved by a partial stroke by adjusting the strength of the electric current for supplying power to the magnet structure group, so that the closing member is lifted from the main valve seat, and the electromagnetic valve is quasi-steady type It is driven in a partially opened state. For example, the current intensity for short pulses is adjusted by presetting the pulse width modulation ratio (PWM ratio). In this way, the solenoid valve according to the invention is opened only up to a predetermined partial stroke which, unlike the switching control valve, is not perfect and is variable with the adjusted current intensity. This allows a pressure-reducing step that can be metered more finely than in a pure switching control valve and thus improves the noise characteristics.

  According to the embodiment of the electromagnetic valve according to the present invention, the mover is configured as an intrusion-type mover, and the intrusion-type mover has a one-stage type together with the magnetic pole core configured corresponding to the mover. Alternatively, a multistage intrusion step portion is formed. Alternatively, the mover may be configured as a flat mover cooperating with a magnetic pole core having a flat magnetic pole surface. In this embodiment, the corresponding magnetic force has a flat characteristic curve from the time when the air gap between the mover and the magnetic pole core reaches a predetermined width.

  According to another embodiment of the solenoid valve according to the invention, the return spring for supplying spring force has a large spring constant. The return spring has a spring characteristic curve designed in a linear shape having a constant spring constant, for example.

  As the air gap decreases as the stroke increases, the characteristic curve gradient of the magnetic force over the stroke also increases, which limits the adjustable region to a small stroke, so the return spring is selectively supplied by the return spring. The applied spring force is configured to have a progressive characteristic curve over the stroke of the mover and the closure member. This means that the spring constant of the return spring is changed between a closed position and an open position in relation to the stroke of the mover and the closing member. The progressive characteristic curve of the spring force improves the stability characteristics of the mover with the closing member and widens the stable working area, in which case the progressive characteristic curve of the spring force is a magnetic characteristic that increases with stroke Overcompensate the curve slope. The progressive spring force characteristic curve of the return spring produces a negative full power characteristic curve slope over an increased stroke area in an advantageous manner. Moreover, small spring constants and small strokes allow greater tolerances of the components, thereby facilitating mass production.

  According to another embodiment of the solenoid valve according to the present invention, the characteristic curve of the fluid force generated by the fluid flow between the first and second flow-through openings is the movable element and the closure member. Is set as flat as possible by the preset flow geometry for the closure member and the main valve seat over the stroke. The flat characteristic curve of the fluid force over the stroke of the mover and the closing member is given in advance by a small opening angle between the closing member and the main valve seat, for example. For this purpose, the sealing region of the closing member is configured in a spherical shape or in a conical shape, whereas the sealing region of the main valve seat is configured in a hollow conical shape.

  In order to facilitate understanding of the preferred embodiments of the present invention described below, as well as the embodiments of the present invention, the above-described conventional embodiments are shown in the drawings below. In the drawings, constituent members or members having the same or similar functions are denoted by the same reference numerals.

It is a schematic sectional drawing of the conventional solenoid valve closed in a non-excited state. 1 is a schematic cross-sectional view of a first embodiment of a valve cartridge of a solenoid valve according to the present invention, which closes in a non-excited state. FIG. 4 is a schematic cross-sectional view of another part of the first embodiment of the valve cartridge of the solenoid valve according to the present invention, which is closed in a non-excited state. FIG. 4 is a schematic cross-sectional view of another part of the first embodiment of the valve cartridge of the solenoid valve according to the present invention, which is closed in a non-excited state. FIG. 6 is a schematic cross-sectional view of a second embodiment of the valve cartridge of the solenoid valve according to the present invention, which is closed in a non-excited state. FIG. 6 is a schematic cross-sectional view of another part of the second embodiment of the valve cartridge of the solenoid valve according to the present invention, which closes in a non-excited state. FIG. 6 is a schematic cross-sectional view of another part of the second embodiment of the valve cartridge of the solenoid valve according to the present invention, which closes in a non-excited state. It is a diagram which shows the controllable power characteristic curve of the solenoid valve of a conventional type and the solenoid valve by this invention. FIG. 4 is a schematic diagram of a spring constant of a return spring that varies over the spring stroke for the solenoid valve of the present invention.

As shown in the diagram of FIG. 4, the conventional solenoid valve 1 configured as a switching control valve through which fluid flows in the closing stroke direction has a magnetic force schematically shown in the first stage of FIG. 4. It has characteristic curves of F _Magnet , spring force F _Feder and fluid force F _Hydraulik . The solenoid valve 2 configured as a steady valve (Stetigventil) through which fluid flows in the direction of the open stroke is composed of a magnetic force F _Magnet , a spring force F _Feder and a fluid force F _Hydraulik , schematically shown in the second stage of FIG. It has a characteristic curve. The electromagnetic valve 3 configured as a steady valve through which fluid flows in the closed stroke direction according to the present invention is schematically shown in the third stage of FIG. 4, the magnetic force F _Magnet , the spring force F _Feder and the fluid force F. _It has the characteristic curve of _Hydraulik . As shown in the third row in FIG. 4, the power characteristic curve of the magnetic force F _Magnet is substantially flat (flat) over the stroke. The return spring may be configured as steep as possible. That is, the return spring 26 may have high spring rigidity. The power characteristic curve of the fluid force F _Hydraulik may be as flat as possible over the stroke as well. The illustrated characteristic curves of the magnetic force F _Magnet , the spring force F _Feder and the fluid force F _Hydraulik based on the stroke characteristic curves of the mover and the closing member are, according to the present invention, the closed and open positions of the mover and the closing member. In such a way that at least one stable working point is adjusted. The working point represents a balance point of force with the negative full power characteristic curve slope. The full power characteristic curve slope for the solenoid valve according to the present invention is obtained from the following equation (1).

As shown in FIGS. 2a to 2c, the first embodiment of the valve cartridge 22 for the solenoid valve according to the present invention is similar to the conventional solenoid valve 1 shown in FIG. A valve insert 25 connected to the magnetic pole core 23, and a mover 24 (coupled to a closing member 28) guided in an axially movable manner between a closed position and an open position in the valve insert 25 And a valve body 29 connected to the valve insert 25. The valve body 29 has a main valve seat 30 arranged between at least one first through-opening 31 and second through-opening 32. A movable element 24 that is movable in the axial direction in the valve insert 25 and a closing member 28 generate a magnetic force F _Magnet that moves toward the magnetic pole core 23 against the spring force F _Feder and fluid force F _Hydraulik of the return spring 26. In order to fix, the magnet structure group shown in FIG. 1 is used. Due to the magnetic force F _Magnet generated by supplying power to the magnet structure group, the mover 24 is moved toward the magnetic core 23, and the closing member 28 is lifted from the main valve seat 30, thereby at least one first The fluid flow between the flow-through opening 31 and the second flow-through opening 32 is adjusted. The spring force F _Feder of the return spring 26 and the fluid force F _Hydraulik generated by the pressure distribution acting on the mover 24 and the closing member 28 by the fluid flow between the first through-flow opening 31 and the second through-flow opening 32. Thus, the mover 24 is lifted from the magnetic core 23 in the valve insert 25, pressing the closing member 28 against the main valve seat 30, and between the at least one first through-flow opening 31 and the second through-flow opening 32. Shut off fluid flow. The characteristic curves associated with the strokes of the magnetic force F _Magnet , the spring force F _Feder and the fluid force F _{Hydraulik depend on} the geometry of the mover 24 and magnetic pole core 23, on the design of the return spring 26 and on the first through-flow opening 31. And the geometry for the flow path between the second through-flow opening 32 and the second through-flow opening 32.

As shown in FIG. 2 b, the mover is configured as an intrusion-type mover 24, which cooperates with a correspondingly configured magnetic core 23 and has two intrusion stages. 22.1 is formed. As shown in FIG. 2b, the interstitial mover 24 has two mover stages 24.1 and the magnetic core 23 has two corresponding magnetic pole stages 23.1. These magnetic core stages 23.1 penetrate into the mover stage 24.1. The characteristic curve of the magnetic force F _Magnet generated by supplying power to the magnet structure group 13 by being configured as the two-stage intrusion stage 22.1 is desired over the strokes of the mover 24 and the closing member 28. To be as flat as possible. In an alternative embodiment not shown, the mover is configured as a flat mover, which cooperates with a magnetic pole core having a flat pole face. However, in such a selective configuration, a characteristic curve with a flat corresponding magnetic force is obtained after the width of the air gap between the mover and the magnetic core becomes a predetermined width.

As shown in FIG. 2c, the sealing region 28.1 of the closing member 28 is configured in a spherical shape, and the sealing region 30.1 of the main valve seat 30 is configured in a hollow conical shape. With this configuration, in this embodiment, a small opening angle is formed between the closing member 28 and the main valve seat 30, and this small opening angle allows the closing member 28 to move between the closing position and the opening position. The desired flat characteristic curve of the fluid force F _Hydraulik is obtained over the stroke of the child.

As shown in FIGS. 3a to 3c, a second embodiment of the valve cartridge 42 for the solenoid valve according to the present invention is shown in FIG. 2a to FIG. As in the first embodiment, the magnetic pole core 43, the valve insert 45 connected to the magnetic pole core 43, and the valve insert 45 are guided to be movable in the axial direction between the closed position and the open position. , And a valve body 49 having a main valve seat 50 connected to the valve insert 45, the valve body 49 having at least one first member. It is arranged between one through-opening 51 and the second through-opening 52. In order to generate the magnetic force F _Magnet , similarly, the magnet structure group shown in FIG. 1 is used. Similar to the first embodiment, the magnetic force F _Magnet , the spring force F _Feder and the fluid force F _{Hydraulik depend on} the given geometry for the mover and magnetic core 43, the design of the return spring 46 and the first This is caused by the given geometry for the flow path between the flow-through opening 51 and the second flow-through opening 52.

As shown in detail in FIG. 3 b, the mover of the second embodiment is also configured as an intrusive mover 44, and this mover 44 cooperates with the corresponding magnetic core 43 in two stages. Intrusion stage 42.1 is formed. As shown in FIG. 3b, the interstitial mover 44 likewise has two mover stages 44.1, and the magnetic pole core has two corresponding magnetic pole stages 43.1. This magnetic core stage 43.1 penetrates into the mover stage 44.1. The characteristic curve of the magnetic force F _Magnet over the stroke of the movable element 44 and the closing member 48 generated by supplying power to the magnet structure group 13 by being configured as the two-stage intrusion stage 42.1 is: Adjust as flat as possible.

As shown in detail in FIG. 3c, the sealing region 48.1 of the closure member 48 is conical and the sealing region 50.1 of the main valve seat 50 is configured as a hollow cone. With such a configuration, a small opening angle is formed between the closing member 48 and the main valve seat 50 in the same manner as in the first embodiment. By this small opening angle, for example, between a closed position and an open position. The desired flat characteristic curve of the fluid force F _Hydraulik is obtained over the stroke of the mover 44 and the closing member 48 between them.

For the above two embodiments of the solenoid valve according to the invention, the return springs 26, 46 for producing the spring force F _Feder have a large spring constant and thus a high spring stiffness. is important. It is particularly advantageous if the spring force F _Feder generated by the return springs 26, 46 has a progressive characteristic over the stroke of the movers 24, 44 and the closure members 28, 48. is there.

By selecting the return springs 26 and 46 whose spring force F _Feder has a progressive characteristic, the stability characteristic of the solenoid valve according to the present invention is improved and the stable working area having a negative full power characteristic curve gradient is expanded. . In this case, the magnetic power characteristic curve gradient that rises with the stroke is overcompensated by the progressive characteristic of the spring force F _Feder . In addition, a spring constant that decreases with a small stroke allows for greater tolerances of the components, thereby facilitating mass production.

As shown in Figure 5, the specific characteristics of the spring constant C _(h), in conjunction with the stroke h, the spring constant C _(h) smallest possible characteristic curves of the min and spring constant C _(h) Located between the maximum possible characteristic curve of max. In addition, the diagram shown in FIG. 5 shows an optimum characteristic curve of the spring constant C _(h) opt. According to FIG. 5, the optimum characteristic curve of the spring constant C _(h) opt is very progressive at a minimum stroke in an advantageous manner, and a stable working point for the corresponding solenoid valve according to the invention. Guarantee existence.

Overall, the solenoid valve according to the invention can produce a desired and well-metered pressure stage with a characteristic curve that rises over a wide flow range. Due to the adjustable steep adjustable stroke of the solenoid valve according to the present invention, the pressure drop is significantly smaller compared to conventional switching control valves. Locally generated pressure vibrations that strongly affect the generated noise are also significantly reduced. For example, a valve current controller that evaluates the pressure sensor signal provides a current flow for generating the magnetic force F _Magnet , so that a desired target characteristic curve gradient for pressure reduction in the wheel brake can be obtained without significant deviation. Thus, smooth wheel pressure adjustment is possible. Moreover, the current intensity for supplying power to the magnet structure group can be adjusted without a pressure sensor. Therefore, it is possible to supply power to the magnet structure group of the electromagnetic valve corresponding to a short pulse time having a variable current intensity that can be adjusted by, for example, providing a pulse width adjustment ratio (PWM ratio) in advance. Unlike the switching control valve, the solenoid valve according to the invention does not open completely but opens up to a predetermined partial stroke which can be changed by the adjusted current strength. This allows a pressure-reducing step that can be metered more finely than in a pure switching control valve and thus improves the noise characteristics.

  The solenoid valve that flows in the direction of the closing stroke according to the invention is advantageous in that it provides a quick valve response, a reduced overall force level and a pressure at any height of the switching control valve that flows in the closing direction. At the same time, it has the advantage of a steady valve.

Claims (11)

A magnet structure group (13), a valve cartridge (22, 42) having a magnetic core (23, 43), a valve insert (25, 45) connected to the magnetic core (23, 43), A movable element (24, 44) guided in a movable manner in the axial direction between a closed position and an open position in the valve insert (25, 45) and connected to a closing member (28, 48); A main valve seat (30, 50) connected to the insert (25, 45) and arranged between the at least one first through-opening (31, 51) and the second through-opening (32, 52). And the movable element (24, 44) movable in the axial direction is supplied with power to the magnet structure group (13). field (25, 45) is caused in the magnetic force (F _Magnet) by a return spring (26, 46) Against the force (F _Feder), and against the fluid force (F _Hydraulik), it is moved in a direction toward the pole center (23, 43), whereby the closure member (28, 48) is Lifted from the main valve seat (30, 50) to allow fluid flow between the at least one first flow-through opening (31, 51) and the second flow-through opening (32, 52); The movable element (24, 44) movable in the axial direction is moved by the spring force (F _Feder ) of the return spring (26, 46) in the valve insert (25, 45). The closing member (28, 48) is airtightly pressed against the main valve seat (30, 50), and the at least one first through-flow opening (31, 51) and the first Between the two flow-through openings (32, 52) In those forms the body flow is adapted to be suspended,
A characteristic curve of the magnetic force (F _Magnet ), a characteristic curve of the spring force (F _Feder ), and a characteristic curve of the fluid force (F _Hydraulik ) over the stroke of the mover (24, 44) are represented by the mover ( 24, 44) and at least one wide and stable working point representing a force balance point with the negative full power characteristic curve slope between the closed and open positions of the closure member (28, 48). Solenoid valve, characterized in that it is combined so that it can be made. A characteristic curve of the magnetic force (F _Magnet ) over the strokes of the mover (24, 44) and the closing member (28, 48) generated by supplying power to the magnet structure group (13) is expressed by the mover (24 44) and the magnetic core (23, 43) are adjusted to be as flat as possible by the given geometry.   By adjusting the intensity of the current for supplying power to the magnet structure group (13), the mover (24, 44) moves together with the closing member (28, 48) over a part of the stroke. Thereby, the closing member (28, 48) is lifted from the main valve seat (30, 50), and the solenoid valve (1) is driven in a semi-steady state, partially open, The electromagnetic valve according to claim 1, wherein the current intensity is adjusted by setting a pulse width adjustment ratio in advance.   The mover is configured as an intrusion-type mover (24, 44), and the intrusion-type mover (24, 44) has a magnetic core (23, 43) configured corresponding to the mover, The solenoid valve according to claim 2 or 3, wherein a single-stage type or a multi-stage type intrusion step part is formed. The mover is configured as a flat mover, and the flat mover cooperates with a magnetic core having a flat magnetic pole surface, and a corresponding magnetic force (F _Magnet ) is applied to the movable element. 4. The solenoid valve according to claim 2, wherein the solenoid valve has a flat characteristic curve from the time when the air gap between the child and the magnetic pole core reaches a predetermined width. 6. The solenoid valve according to claim 1, wherein the return spring (26, 46) for supplying the spring force (F _Feder ) has a large spring constant. The spring force (F _Feder ) supplied by the return spring (26, 46) has a progressive characteristic curve over the strokes of the mover (24, 44) and the closing member (28, 48). The electromagnetic valve according to any one of claims 1 to 6. A characteristic curve of fluid force (F _Hydraulik ) generated by the flow of fluid between the first through-flow opening (31, 51) and the second through-flow opening (32, 52) is expressed by the movable element (24 44) and over the stroke of the closure member (28, 48), the preset flow geometry for the closure member (28, 48) and the main valve seat (30, 50) is possible The solenoid valve according to any one of claims 1 to 7, wherein the solenoid valve is set as flat as possible. A flat characteristic curve of the fluid _force (F _Hydraulik ) over the strokes of the mover (24, 44) and the closing member (28, 48) is expressed by the closing member (28, 48) and the main valve. 9. Solenoid valve according to claim 8, wherein the solenoid valve is preliminarily provided by a small opening angle between the seat (30, 50).   The sealing area (28.1) of the closure member (28) is configured in a spherical shape and the sealing area (30.1) of the main valve seat (30) is configured in a hollow conical shape. The solenoid valve described.   The sealing region (48.1) of the closure member (48) is configured in a conical shape and the sealing region (50.1) of the main valve seat (50) is configured in a hollow conical shape. 9. The solenoid valve according to 9.

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